WO2008090295A2 - Housing for ball bearing - Google Patents
Housing for ball bearing Download PDFInfo
- Publication number
- WO2008090295A2 WO2008090295A2 PCT/FR2007/052519 FR2007052519W WO2008090295A2 WO 2008090295 A2 WO2008090295 A2 WO 2008090295A2 FR 2007052519 W FR2007052519 W FR 2007052519W WO 2008090295 A2 WO2008090295 A2 WO 2008090295A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cage
- heel
- claws
- free spaces
- cells
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6607—Retaining the grease in or near the bearing
- F16C33/6614—Retaining the grease in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/38—Ball cages
- F16C33/41—Ball cages comb-shaped
- F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
- F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
- F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/20—Application independent of particular apparatuses related to type of movement
- F16C2300/22—High-speed rotation
Definitions
- the present invention relates to the field of bearing cages, in particular the cages made of synthetic material used in ball bearings, in particular with deep grooves, in order to ensure the proper circumferential spacing between the balls.
- the invention also relates to bearing cages for high speed operation.
- Such types of cages have a generally annular shape with spherical cells in which the balls are partially housed.
- the balls are held in the cells by claws arranged in pairs opposite the heel of the cage.
- the spherical cells have a diameter slightly greater than that of the balls, so that a certain functional clearance between beads and cells exists.
- the document JP 2003-035 317 (NSK) or the patent application US 2002/1 14550 disclose a cage provided, between two cells, with a deep groove extending from a radial face opposite the claws up to near the claws. Notches are provided from the groove to the bore of the cage.
- the object of the invention is to remedy these drawbacks.
- the invention also aims to reduce the radial deformations of the end of the cage opposite the heel while helping to improve the circulation of the lubricant inside the bearing.
- the ball bearing cage comprises a generally annular shaped body and claws.
- the body comprises a heel of substantially annular shape and a substantially axial portion connecting to the heel and in which are formed cells for the balls.
- the substantially axial portion supports said claws on the axially opposite side to the heel.
- the outer diameter of the bead is greater than that of the axial portion so that said axial portion is thinner radially than the bead.
- the cage comprises an axial partition disposed between the cells and extending axially from the end of the heel opposite the claws to the claws radially delimiting external and internal free spaces located radially on either side of said partition.
- the cage is thus lightened while creating lubricant reservoirs and circulation channels.
- a structure is particularly advantageous because of the existence of a heel of greater thickness and an axial partition which extends axially from the outer cylindrical surface of the heel opposite the claws, to the claws, so as to define outside and inside free spaces.
- the outer space preferably opens on each side of the heel so as to improve lubrication.
- the outer free spaces form cavities axially crossing the heel of the cage and opening axially on both sides of said heel.
- the lubricant can move to the rolling elements.
- the inner free spaces form recesses open axially towards the face of the heel opposite the claws and radially inward. A large amount of lubricant can be stored there.
- the axial partition comprises at least one opening allowing communication between the outer free spaces and the inner free spaces facing each other.
- Said opening may have the shape of a notch formed in the axial partition from the end of the heel opposite the claws.
- the axial partition extends between the cells in the circumferential direction and is disposed substantially in a circle. Stiffening of the cells is thus ensured.
- the fact that the partition extends from the outer surface of the heel opposite the claws to the base of the claws ensures excellent rigidity of the cage.
- the outer diameter of the axial partition is substantially equal to the pitch diameter of the cage.
- the outer diameter of said substantially axial portion is smaller than the outer diameter of the heel.
- the rolling bearing may comprise balls mounted in the cells of a cage and disposed between two raceways.
- two different lubricants are disposed, at least one being positioned in the inner free spaces.
- the grease can flow axially through the inner and outer free spaces to return to the vicinity of the balls.
- the internal free spaces form at the same time fat reserves located near the balls and thus allowing the grease to slowly diffuse lubricant towards the balls.
- the free spaces form channels allowing the free axial circulation of the grease between the two sides of the bead of the cage, which greatly improves the general lubrication.
- the general structure of the cage is lightened, thereby saving material and reducing the weight of the cage which is interesting for many applications and whose The effect is also to reduce the centrifugal effect of high speeds of rotation.
- the cage is rigid thanks to the ribs formed by the cell edges and the axial wall connecting the cell edges and extending from the end of the opposite heel to the claws to the base of the claws.
- the zone of contact between the balls and the cells being substantially at the radial level of the axial partition, the circumferential forces due to the impacts generated by the balls on the cells during operation are thus taken up by said partition and do not cause no significant deformations or noticeable local constraints of the cage.
- an axial thickness identical to that of the interior of the cell can be maintained, thus forming a rib providing good rigidity.
- the weight gain of a cage can be of the order of 20 to 30%, for example 25%, while the radial deformation can be reduced by about 30 to 40%, for example
- a bearing can be used at a speed of rotation that is 17% greater than a bearing equipped with a conventional cage, for example 700 000 ndm instead of 600 000 ndm, the ndm being a speed factor resulting from the produces rotational speed in rpm by the pitch diameter of the bearing in mm.
- the ndm is representative of the linear speed of movement of the balls.
- the cage also allows, for a given speed, use with higher operating temperatures than in the case of a conventional cage, and this thanks to the reduction of the deformation and increased space available for the lubricant.
- the operating temperature limit can be extended from 120 ° C. to 150 ° C.
- reducing the amount of material forming the cage has a significant effect of reducing the cost of raw material.
- FIG. 1 is a perspective and exploded view of a rolling bearing according to one aspect of the invention
- Figure 2 is another perspective view of the bearing of Figure 1
- - Figure 3 is a perspective view of a rolling bearing cage presented from the front
- Figure 4 is a perspective view of another cage presented from the rear
- Figure 5 is a half-view in cross-section through an axial plane of the cage of Figure 3
- Figure 6 is a detail view of the cage of Figure 3
- Figure 7 is a partial rear view of a cage according to another embodiment
- - Figure 8 is a partial perspective view of the cage of Figure 7.
- the rolling bearing comprises an outer ring 1, an inner ring 2, a row of rolling elements 3, here balls, and a cage 4 for maintaining the circumferential spacing of the elements.
- Sealing flanges or seals may be attached to the outer ring 1 and provide a frictional or narrow seal with an inner ring surface 2.
- the outer rings 1 and inner 2 are of the deep groove type, for example obtained by machining a portion of a tube or a ring blank forged or laminated.
- the outer ring 1 comprises a cylindrical axial outer surface 1a, opposite radial end surfaces 1b and 1c, and a bore from which is formed a raceway 1d for the rolling elements 3.
- the inner ring 2 comprises a cylindrical bore 2a, two opposite radial frontal surfaces 2b and 2c and an outer surface from which is formed a rolling track 2d for the rolling elements 3.
- the outer ring 1 is provided with two symmetrical grooves in which the flanges of sealing, on the side of the radial surface Ib and the radial surface I c.
- the cage 4 is better visible in Figures 3 and 4 and comprises a body 5 of generally annular shape and claws 6.
- the cage 4 may be a single piece, for example molded polyamide, by injection such as PA 6.6.
- the body 5 comprises a heel 7 of generally annular shape and an axial portion 8 defining a plurality of cells 9 for the rolling elements 3.
- the cells 9 are spherical or quasi-spherical.
- the claws 6 also contribute to defining the cells 9.
- the heel 7 has an outer diameter greater than that of the axial portion 8 and a substantially equal inner diameter.
- a bead having an inside diameter slightly different from that of the axial portion 8 could be provided.
- the axial portion 8 has an axial length at least equal to the half of the diameter of the cells 9, so that that the rolling elements 3 can be properly retained in the cells 9.
- the outer diameter of the substantially axial portion 8 is close to the pitch diameter of the cage, for example in the range defined between the pitch diameter of the cage minus the thickness radial of the heel and the primitive diameter of the cage plus half of the radial thickness of the heel.
- the pitch diameter of the cage is the diameter of the fictitious circle passing through the center of the fictitious spheres defining the cells 9.
- the axial portion 8 forms a protuberance comprising two branches 10 in an arc of a circle each terminating in a claw 6 opposite the heel 7.
- the axial portion 8 also comprises a rib 12 connecting the ends of the branches 10 associated with two adjacent cells, axially opposite the heel
- the rib 12 provides a spacer function. Beyond the rib 12, extend the claws 6.
- the branches 10, the claws 6 and the rib 12 may have a substantially equal radial thickness.
- the branches 10 form ribs with a sufficient surface to define the cells 9 retaining the rolling elements 3.
- the branches 10 may have a substantially constant thickness from a rib 12 to the next rib 12.
- the cage 1 also comprises a connection 13 situated at the base of each leg 10 and forming an interface between the heel 7 and the leg 10.
- the connection 13 has a rounded profile in cross-section and has a decreasing radial thickness going from heel 7 towards the branch 10.
- the connection 13 may have an axial length of the order of 15 to 30% of the axial length of the substantially axial portion 8.
- the cage also comprises an axial partition 14 connecting two branches 10 of two neighboring cells 9.
- the axial partition 14 has a small radial thickness, for example less than half the radial thickness of the branches 10, and extends axially between the base surface or outer cylindrical surface 7a of the heel 7 and the base of the claws 6.
- the partition 14 is disposed at a radial distance from the internal face of the axial portion 8 and is substantially flush with the outer periphery of said axial portion 8, leaving free internal spaces 15 and outer free spaces 16 as can be seen on the drawings. Figures 3, 5 and 6.
- the partition 14 may be slightly recessed radially relative to the periphery of the axial portion 8 as in Figure 4.
- the internal free spaces 15 extend axially between the rib 12 and the end face 7a of the heel 7 on which said internal free spaces 15 open.
- the spaces The inner free spaces 15 are delimited radially outwards by the axial partition 14 and open inwards into the bore of the cage 4.
- the internal free spaces 15 are also defined in the circumferential direction by the branches 10 of two neighboring cells. 9.
- the internal free spaces 15 pass through the heel 7 and at least partially the substantially axial portion 8.
- the free spaces 16 are formed in the heel 7 and in the connection 13, see more particularly Figures 5 and 6.
- the outer free spaces 16 are in the form of an arcuate slot according to the general curvature of the heel 7 opening on the end surface 7a of the heel 7 by an oblong opening and opening on the opposite side in the connection 13 by an equally oblong opening.
- the outer free spaces 16 may extend axially over the periphery of the axial portion to form cuvets 16a radially recessed with respect to the outer edge of the cells (see Figure 4).
- the radial dimension of the outer free spaces 16 can be reduced by going from the end surface 7a of the heel 7 to the connection 13, see FIG. 5.
- the angular dimension of the outer free spaces 16 can decrease by going from end surface 7a of the heel 7 to the connection 13.
- the outer free spaces 16 may be located slightly beyond the pitch diameter of the cage 4.
- the outer free spaces 16 are formed radially beyond the branches 10 which can maintain a high rigidity.
- the pitch diameter of the cage may be flush with the outer surface of the substantially axial portion 8.
- the heel 7, angularly at the level of the outer free spaces 16, is divided into two rings, radially spaced inner 17 and outer 18, thus making it possible to leave said external free spaces
- the rings 17 and 18 which start from the outer base surface 7a of the heel 7, meet at the right of the cells 9 by merging with the branches 10 to form a common trunk.
- the balls mainly come into contact with an area 19 of the cells 9 which is relatively limited in area and located axially at the level of the ribs 12.
- the forces exerted by a ball on the contact zone 19 a cage 4 is therefore taken over, not only by the corresponding branch 10, but also by the rib 12 and the branch 10 of the next cell.
- the force exerted along a tangent to the cell 9 is also taken up by the axial partition 14.
- the cage 4 thus has excellent rigidity to the circumferential forces exerted by the balls on said cages.
- the recessed structure of the cage 4 in particular thanks to the free spaces 15 and 16, allows a lightening of the mass of the cage 4 by reducing the quantity of material used, hence a reduction of the centrifugal forces during a high speed rotation.
- the radial rigidity is nevertheless quite satisfactory, especially thanks to the ribs 12 and the branches 10 which have a significant radial thickness. This prevents annoying deformation of the cage 4 towards the outside, in particular at the level of the claws 6.
- the presence of the internal free spaces 15 makes it possible to have a large reserve of lubricant close to the cells 9 and the rolling elements 3
- the outer free spaces 16 may also provide a lubricant reservoir function and a lubricant circulation channel function from the end surface 7a side of the bead 7 to the connection 13.
- the lubricant emerging from the opening of the the external free space 16 in the connection 13 can either move outwards by centrifugal effect and join the race I d of the outer ring 1, or move angularly and join the rolling elements 3 arranged in the cells 9 .
- Notches 20 are formed in the axial partition 14 from the end surface 7a of the heel 7.
- notches 20 form an interruption in the inner ring 17.
- the notches 20 put in communication the internal free spaces 15 and outer 16 and this, in the overall size of the cage 4, and thus allow a lubricant circulation of space free interior 15 to the internal free space 16 and therefore, a better circulation of the lubricant to the raceway I d of the outer ring 1 or to the rolling elements 3 disposed in the cells 9.
- the notches 20 are found particularly useful in the case where the axial distance between the end surface 7a of the heel 7 and the sealing flange of the bearing is low, which is often the case in compact bearings.
- a lubricant for example a grease
- a low-life lubricant is provided on the outside of the cage, in particular in the outer free spaces 16 and a long-life lubricant on the bore side of the cage, Particularly in internal clearances 15.
- the low-life lubricant is centrifuged to the outer race I d as soon as the bearing is rotated to ensure immediate lubrication.
- the long-life lubricant takes over the low-life lubricant by diffusing more slowly through the bearing.
- the low-life lubricant is disposed outside the cage and the long-life lubricant is disposed in the inner and outer free spaces 16.
- the lubricants may be greases of different viscosities.
- the cage also has the advantage of facilitating the cleaning of the bearing, a step that takes place after the establishment of the cage, during the assembly process. Indeed, the cleaning liquid introduced into the bearing can circulate more easily between the outer ring 1 and inner 2 and thus more effectively cause polluting particles that could otherwise remain in the bearing and be detrimental to its proper operation.
- the axial partitions 14 are stiffened radially by the branches 10 and the ribs 12 which have a much greater radial thickness. The cage is therefore suitably stiffened both in the radial direction and in the angular direction.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2007800502576A CN101627217B (en) | 2007-01-26 | 2007-12-14 | Housing for ball bearing |
JP2009546787A JP5441713B2 (en) | 2007-01-26 | 2007-12-14 | Housing for ball bearing |
US12/449,120 US8454240B2 (en) | 2007-01-26 | 2007-12-14 | Cage for ball bearing |
DE112007003280T DE112007003280T5 (en) | 2007-01-26 | 2007-12-14 | Cage for ball bearings |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0752908A FR2911934B1 (en) | 2007-01-26 | 2007-01-26 | CAGE FOR BALL BEARING |
FR0752908 | 2007-01-26 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2008090295A2 true WO2008090295A2 (en) | 2008-07-31 |
WO2008090295A3 WO2008090295A3 (en) | 2008-10-09 |
Family
ID=38344735
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2007/052519 WO2008090295A2 (en) | 2007-01-26 | 2007-12-14 | Housing for ball bearing |
Country Status (6)
Country | Link |
---|---|
US (1) | US8454240B2 (en) |
JP (1) | JP5441713B2 (en) |
CN (1) | CN101627217B (en) |
DE (1) | DE112007003280T5 (en) |
FR (1) | FR2911934B1 (en) |
WO (1) | WO2008090295A2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101886671A (en) * | 2009-05-16 | 2010-11-17 | 谢夫勒科技有限两合公司 | Rolling bearing |
EP3267057A1 (en) * | 2016-07-06 | 2018-01-10 | Regal Beloit America, Inc. | Bearing retainer, bearing and associated method |
Families Citing this family (29)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102010035061A1 (en) * | 2010-08-21 | 2012-02-23 | Schaeffler Technologies Gmbh & Co. Kg | Double comb cage for a double-row cylindrical roller bearing with mass balance |
JP5615649B2 (en) * | 2010-09-28 | 2014-10-29 | Ntn株式会社 | Ball bearing |
DE112010006035T5 (en) | 2010-11-30 | 2013-08-29 | Aktiebolaget Skf | Comb cage for ball bearings and ball bearings with such a cage |
FR2994722B1 (en) | 2012-08-22 | 2015-05-22 | Skf Ab | CAGE FOR BEARING, IN PARTICULAR FOR MOTOR VEHICLE ELECTRIC DIRECTION BEARING |
FR2994720B1 (en) * | 2012-08-22 | 2015-07-03 | Skf Ab | CAGE FOR BEARING BEARING, BEARING BEARING AND ELECTRIC DIRECTION OF MOTOR VEHICLE |
FR2994721B1 (en) | 2012-08-22 | 2015-07-03 | Skf Ab | CAGE FOR BEARING BEARING, BEARING BEARING AND ELECTRIC DIRECTION OF MOTOR VEHICLE |
FR2996889B1 (en) | 2012-10-12 | 2015-04-24 | Skf Ab | CAGE FOR BEARING, IN PARTICULAR FOR MOTOR VEHICLE ELECTRIC DIRECTION BEARING |
FR2998631B1 (en) | 2012-11-27 | 2015-09-04 | Skf Ab | CAGE FOR BEARING, IN PARTICULAR FOR MOTOR VEHICLE ELECTRIC DIRECTION BEARING |
FR3001511B1 (en) | 2013-01-25 | 2016-02-26 | Skf Ab | CAGE FOR BEARING, IN PARTICULAR FOR MOTOR VEHICLE ELECTRIC DIRECTION BEARING |
FR3001510B1 (en) | 2013-01-25 | 2016-07-01 | Skf Ab | CAGE FOR BEARING, IN PARTICULAR FOR THE ELECTRIC DIRECTION BEARING OF A MOTOR VEHICLE |
FR3007808B1 (en) | 2013-06-28 | 2015-07-17 | Skf Ab | CAGE FOR BEARING, IN PARTICULAR FOR THE BEARING OF ELECTRIC POWER STEERING SYSTEM OF A MOTOR VEHICLE |
DE102014212531A1 (en) * | 2013-07-23 | 2015-01-29 | Schaeffler Technologies Gmbh & Co. Kg | Bearing cage with grease reservoirs for self-lubrication |
WO2015031247A2 (en) * | 2013-08-27 | 2015-03-05 | The Timken Company | Retainer |
DE102014201442A1 (en) | 2014-01-28 | 2015-07-30 | Schaeffler Technologies AG & Co. KG | Ball snap cage |
US9546682B2 (en) * | 2014-12-09 | 2017-01-17 | Aktiebolaget Skf | Cage of a rolling bearing, rolling bearing comprising such a cage and apparatus comprising such a rolling bearing |
US10280668B2 (en) * | 2015-08-14 | 2019-05-07 | Unique Garage Door Inc. | Garage door noise reduction roller assembly |
US9945421B2 (en) * | 2016-07-06 | 2018-04-17 | Regal Beloit America, Inc. | Bearing retainer, bearing and associated method |
DE102017115881A1 (en) * | 2017-05-10 | 2018-11-15 | Schaeffler Technologies AG & Co. KG | Rolling bearing cage |
FR3086024B1 (en) * | 2018-09-17 | 2021-02-26 | Valeo Embrayages | DRY PENDULUM CUSHIONING DEVICE |
US10605307B1 (en) * | 2018-11-02 | 2020-03-31 | Regal Beloit America, Inc. | Bearing retainer, bearing and associated method |
CN110231146B (en) * | 2019-05-25 | 2021-12-07 | 深圳市华芯技研科技有限公司 | Binocular is lens detection calibration equipment for camera |
US11078959B1 (en) * | 2020-06-10 | 2021-08-03 | Schaeffler Technologies AG & Co. KG | High speed bearing with single piece wide plastic cage |
US11286988B2 (en) * | 2020-07-27 | 2022-03-29 | Schaeffler Technologies AG & Co. KG | Single-piece high-speed bearing cage |
IT202000021943A1 (en) | 2020-09-18 | 2022-03-18 | Skf Ab | BEARING CAGE AND BEARING |
DE102021100612B3 (en) | 2021-01-14 | 2022-04-28 | Schaeffler Technologies AG & Co. KG | Roller bearing of a scroll compressor with optimized lubrication |
JP7420274B2 (en) * | 2021-01-18 | 2024-01-23 | 日本精工株式会社 | Crown cage for ball bearings and ball bearings |
CN115750597A (en) * | 2021-09-03 | 2023-03-07 | 斯凯孚公司 | Bearing cage and rolling bearing having the same |
DE102022102659A1 (en) | 2022-02-04 | 2023-08-10 | Schaeffler Technologies AG & Co. KG | roller bearing |
WO2023203902A1 (en) * | 2022-04-20 | 2023-10-26 | 日本精工株式会社 | Crown-type retainer for ball bearing, and ball bearing |
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JP2003269465A (en) * | 2002-03-13 | 2003-09-25 | Nsk Ltd | Ball bearing |
JP2003287032A (en) * | 2002-03-28 | 2003-10-10 | Nsk Ltd | Plastic made crown type holder for ball bearing |
JP4188666B2 (en) * | 2002-11-15 | 2008-11-26 | Ntn株式会社 | Resin cage for rolling bearings |
FR2900996B1 (en) * | 2006-05-12 | 2008-08-08 | Skf Ab | CAGE FOR BALL BEARING |
-
2007
- 2007-01-26 FR FR0752908A patent/FR2911934B1/en not_active Expired - Fee Related
- 2007-12-14 WO PCT/FR2007/052519 patent/WO2008090295A2/en active Application Filing
- 2007-12-14 DE DE112007003280T patent/DE112007003280T5/en not_active Withdrawn
- 2007-12-14 JP JP2009546787A patent/JP5441713B2/en not_active Expired - Fee Related
- 2007-12-14 CN CN2007800502576A patent/CN101627217B/en not_active Expired - Fee Related
- 2007-12-14 US US12/449,120 patent/US8454240B2/en not_active Expired - Fee Related
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US4938613A (en) * | 1989-07-24 | 1990-07-03 | General Motors Corporation | Moldable plastic bearing ball retainer |
US20020114550A1 (en) * | 1999-07-14 | 2002-08-22 | Minebea Co., Ltd. | Retainer for rolling bearing |
JP2003035317A (en) * | 2001-07-24 | 2003-02-07 | Nsk Ltd | Crown type retainer of synthetic resin and rolling bearing |
JP2003329045A (en) * | 2002-05-13 | 2003-11-19 | Nsk Ltd | Hybrid car drive motor and roller bearing therefor |
JP2005214259A (en) * | 2004-01-28 | 2005-08-11 | Nsk Ltd | Ball bearing and ball bearing for alternator |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101886671A (en) * | 2009-05-16 | 2010-11-17 | 谢夫勒科技有限两合公司 | Rolling bearing |
US8622622B2 (en) | 2009-05-16 | 2014-01-07 | Schaeffler Technologies AG & Co. KG | Antifriction bearing |
EP3267057A1 (en) * | 2016-07-06 | 2018-01-10 | Regal Beloit America, Inc. | Bearing retainer, bearing and associated method |
Also Published As
Publication number | Publication date |
---|---|
JP5441713B2 (en) | 2014-03-12 |
DE112007003280T5 (en) | 2010-03-04 |
CN101627217B (en) | 2012-08-29 |
US8454240B2 (en) | 2013-06-04 |
FR2911934A1 (en) | 2008-08-01 |
CN101627217A (en) | 2010-01-13 |
JP2010516967A (en) | 2010-05-20 |
WO2008090295A3 (en) | 2008-10-09 |
FR2911934B1 (en) | 2009-09-18 |
US20100142874A1 (en) | 2010-06-10 |
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